FI102003B - Deflection adjustable roller - Google Patents

Description

102003

Böjningsreglerbar Vals 5 deflection roller

The invention relates to a deflection-adjustable roll intended to form a nip with a counter-roll, the deflection-adjustable roll comprising a stationary roll shaft rotatably arranged around a roll shell, between which the roll shell and the roll axis are provided with hydraulic pressure means acting on the inner surface of the roll shell and supported on the roll shaft. loading elements comprising cylindrical bores or similar cavities formed in the roll shaft and load shoes supported on the inner surface of the roll shell by means of an oil film, the piston parts of which are movably arranged in the radial direction of the roll. that the line load on the nip is adjustable pressure in accordance with the media, the pressure.

A variety of deflection-adjustable rolls for paper machine or paper finishing devices are known in the art, and various names are used, such as deflection-compensated roll, zone-adjustable roll, and the like. These rolls usually comprise a massive: or tubular, stationary roll shaft and a roll shell • · · · · rotatably arranged around it. Between the axis of said roll and the shell is arranged on the inner surface of the shell I * f; | effective slipper arrangements and / or a pressurized fluid chamber or chamber set so that the axial profile of the roll shell can be adjusted or adjusted as desired at the nip.

| The present invention relates in particular to a deflection-adjustable roll in which the axial profile of the roll shell is adjusted by means of sliding shoes acting on the inner surface of the roll shell. by means of arrangements which sliding shoe arrangements are loaded against the inner surface of the roll shell • · ·. ·: ·. by means of a hydraulic pressure medium.

• · · * • · «·« • · «**.!. * 30 When using a deflection-adjustable roller with small line loads, it becomes a problem to adjust the pressure of the hydraulic load elements. This problem is mainly due to the fact that the hydraulic control accuracy of • · · • · · *; * * is quite poor near the O pressure. The adjustment accuracies of the valves and pressure sensors used in hydraulic systems • · • · 2 102003 are not sufficient for precise adjustment at very low pressures, and in addition the valves and sensors experience "creep", which means that the hydraulic system has to be calibrated quite often. This frequent need for calibration poses an additional problem to the system that the operating temperature of the roll 5 may differ significantly from the calibration temperature. In this case, this temperature change between the calibration temperature and the operating temperature may cause an even larger error in the adjustment of the line load of the roll than the adjustable pressure. Such low line rolls, which exhibit the problems described above, are used in particular in paper machine twin roll calenders.

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Another significant problem associated with low line loads driven by hydraulically loaded deflection controlled rollers is due to the control of the roll temperature as well as the need for lubrication of the hydraulic load elements. When loading the roller casing with hydraulic load elements, part of the hydraulic pressure oil used for loading is normally routed through capillary bores arranged in the load shoe of the load elements into pockets formed on the outer surface of the load shoe. When the roll is driven with very .. small line loads, the consequence is that the load elements pass through the load elements. . The amount of oil flowing between the pressure shoes and the inner surface of the roll shell is very small, which endangers the lubrication of the load shoes. Furthermore, these small amounts of oil flowing through the load elements cause problems with the heating of the roll. Specially • · · • · ·*.*. to achieve a uniform cross-machine temperature profile I · • · usually requires quite large amounts of oil, so that in addition to lubrication, these oil flows also have a cooling effect. Current low line rollers have lubrication ♦ *. In order to ensure and achieve a cooling effect, it was necessary to use a separate oil supply from the hydraulic oil system of the hydraulic: * · * load elements.

• · • »· •» »I I · ·, ···. With regard to the state of the art, reference is also made to Finnish patent No. 79 178, which is an earlier FI patent of • · · 30 applicants and relates to a method for leveling the temperature profile of a deflection-adjustable roll and a roll for carrying out the method. Ko. The roll according to the patent «· • · · 102003 3 comprises, in addition to the actual load elements of the roll, so-called rolls arranged in certain areas of the roll and acting in opposite directions. only zone elements, which are used especially in cases where a very low, sometimes even negative line pressure must be reached in the roll nip. Since the counter-zone elements and the actual load elements at their 5 together would cause a considerable temperature rise in the roll temperature profile, in the roll according to FI patent no. 79 178 the counter-zone elements and the actual load elements at them are connected to each other hydraulically or mechanically. The coupling is such that when the inner surface of the roll shell is loaded with counter-zone elements, the actual load elements 10 at the corresponding position are completely pulled away from affecting the inner surface of the roll shell. The temperature profile can be equalized with this arrangement. For very small line loads, the with the arrangement according to the patent to reach without counter-zone elements.

The object of the present invention is to avoid the disadvantages of the prior art 15 described above and to provide a deflection-adjustable roll which does not have similar problems in control accuracy, but in which the control accuracy is significantly better than before and in which there is no lubrication or temperature problem. To achieve this, the deflection-adjustable roll according to the invention is mainly characterized in that each hydraulic of the deflection-adjustable roll. A flange member extending in the radial • · f t · direction of the piston part is formed in the piston part of the load shoe of the load element 20 and is respectively in the cylinder bores or the like • «| a mating piece adapted to the cavities, having a flange extending radially • · 0 ··. ·] in the opposite direction to the flange member of the piston part, the piston part and the mating piece being S · • «. ·: ·. slidably sealed relative to each other through said flange member and the flange, defining an annular space therebetween which is sequenced to be subjected to a continuous load in the opposite direction to the load direction of the hydraulic load elements, which} '· *; together with the desired nip pressure determines the hydraulic load elements. the magnitude of the applied load pressure.

119 • · · · o.;. The invention achieves significant advantages over the prior art, and of these advantages it is possible to highlight in this connection e.g. following. In the roll according to the invention, a constant force acting on the hydraulic loading elements in the opposite direction to the compression direction is produced, whereby the pressure of the pressure oil used for pressurizing the hydraulic loading elements can be considered to be substantially higher than without the above-mentioned constant force. The pressure of the pressurized oil can be up to several tens of times compared to the rollers driven by modern technology with low line loads. This, in turn, has the direct consequence that the control accuracy is significantly better than in the past due to the higher pressures used. The invention makes the operating range of the roll substantially wider, because by adjusting the constant counterforce used in the hydraulic loading elements to different levels, the operation of the roll 10 can be optimized over a wide line load range. A significant advantage of the invention is further that the amount of oil consumed by the roll is made higher than in previously known rollers driven with low line loads, as a result of which the roll is more even and the lubrication of the hydraulic load shoes is ensured. It is possible to apply the invention in such a way that the oil flow through the hydraulic load elements is made state in each load element or in the zone formed by the load elements, whereby the problems previously encountered with respect to temperature are completely avoided. Other advantages and features of the invention will become apparent from the following detailed description of the invention.

• · *,. Fig. 1 shows in a completely schematic vertical section in the machine direction a deflection-adjustable roll according to the invention, which forms a nip with a counter roll.

Fig. 2 schematically shows, in cross-sectional vertical section of the machine, a deflection-adjustable roll according to the invention and a counter roll forming a nip therewith.

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Figure 3 is a schematic and partial vertical cross-section of a load element according to a preferred embodiment of a deflection-adjustable roll according to the invention.

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Mt 30 Fig. 4 shows a view corresponding to Fig. 3 of another preferred embodiment of a load element used in a deflection-adjustable roll according to the invention.

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Fig. 5 is a schematic view from the direction of the roll shell of a loading shoe of a hydraulic loading element.

102003 5

Fig. 6 shows a view corresponding to Figs. 3 and 4 of a further preferred embodiment of a load shoe for use in a deflection-adjustable roll according to the invention.

In Figures 1 and 2, the deflection-adjustable roll according to the invention is indicated generally by reference numeral 1. In the embodiment of these figures, the deflection-adjustable roll 1 comprises 10 solid roll shafts 3 and a roll shell 2 rotated thereon. Between the roll shaft 3 and the roll shell 2 hydraulic loads acting on the inner whose direction of action is parallel to the nip plane. In the embodiment of Figures 1 and 2, the end bearing of the roll shell 2 and other accessories of the roll 1 are not shown, as they are not substantially related to the invention and thus do not form part of the invention. The shaft 3 of the deflection-controlled roll 1 is supported in a conventional manner by means of articulated bearings 5 on the machine frame. The deflection-adjustable roller 1 forms a nip N with a counter-roller 6, which counter-roller 6 is also mounted on its machine body 7 by means of bearings 8 in a manner known per se by means of bearings 8.

. In the embodiment shown in Fig. 2, the deflection-adjustable roller 1 is divided into zones ZpZ2.Z3.Z4 in the transverse direction of the machine so that the hydraulic load elements 10 belonging to each zone Z! -Z4 0 ·. * I are adjusted zone by zone. Roll 1 is thus »··; ·. · [Being a zone-adjustable roll in the embodiment of the figure. In the embodiment of Figure 2, the roll • 0 • 1 is divided into four zones, but it must of course be understood that the number of zones 25 may be something else. Furthermore, in the embodiment of Figure 2, it is shown that each zone comprises two hydraulic loading elements 10, but is of course «j 'f'; it is clear that the hydraulic loading elements belonging to each zone Z j to Z4. *. The number t 10 may differ from that shown in Figure 2. Reference numeral 9 is shown in the figures

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* · *. The pressure oil channels leading to zones 1 and 2 ZrZ4 and the reference number 9 'denote I 1 f 30 oil channels, i.e. the so-called a back pressure channel, the meaning of which will become apparent in more detail from the description of Figures 3 and 4 of the drawing. As stated earlier, the deflection-adjustable roll 1 shown in Figures 1 and 2 has a massive roll shaft 3, but a roll-like shaft can also be used in the roll 1, in which e.g. the applicant's previous FI patent No. 81 659 oil distribution system in accordance with

Fig. 3 shows a preferred embodiment of a hydraulic loading element for a deflection-adjustable roll according to the invention, which in Fig. 3 is indicated by reference numeral 10a. In Fig. 3, the axis of the deflection-adjusted roll is denoted by reference numeral 3, the roll casing by reference numeral 2 and the inner surface of the roll casing by reference numeral 4.

The hydraulic loading element 10a comprises a loading shoe 11a, which is loaded against the inner surface 4 of the roll shell 4 in a known manner. there is always an oil film between the inner surface 4 of the roll shell. Fig. 5 shows in more detail, for example, the pocket structure of the load shoe 11 according to Fig. 3. The load shoe is indicated by reference numeral 11 in Fig. 5.

The pockets 12a of the load shoe 11 thus comprise recesses 12 formed in the curved surface of the load shoe 11 facing the roll shell, bounded by the longitudinal and transverse edge bases 12 'and the central bases 12', respectively. Oil is thus introduced into these recesses, i.e. the pockets 12, through the capillary bores 13 so that the pockets 12 form a hydrostatic bearing from the load shoe 11, whereby the loads are applied. between the shoe 11 and the inner surface 4 of the roll shell there is an oil mattress or oil film as the roll rotates.

i * »i« · «« * • ·· · *. * * A cavity 14a corresponding to the shape of the outer surface of the load shoe 11a is formed in the roll shaft 3 for each hydraulic loading element 10a. However, said recess 14a has the dimensions of the load shoe 11a. larger so that a clearance is left between the outer surface of the load shoe 11a and the walls of the recess, i.e. the cavity 14a. In the embodiment of Figure 3, the load shoe 11a has shapes. elongated so that said loading shoe 11a protrudes deeply into the recess formed in the shaft 3 of the roll, i.e. the cavity 14a. The load shoe 11a has a cylindrical cavity 24a formed in the axial direction of the load shoe. Over here

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., a mating piece 17a is arranged in the cavity space 24a of the loading shoe 1a, which is fixed to the bottom of the recess, i.e. the cavity 14a formed by the screw thread 18a in the roll shaft 3 so that the mating piece 17a is immovable with respect to the roll shaft 3. A connection to the pressure oil channel 9 opens through the bottom of the screw thread 18a. The mating piece 17a is provided with a flange 19a which is sealed to the wall of the cavity 24a by means of a seal 20a. An inwardly directed flange member 15a is rigidly attached to the lower end of the load shoe 5 11a by a suitable connection, such as a threaded connection 16a or the like, which is sealed to the mating piece 17a by means of a seal 21a. The flange 19a of the mating piece and the flange member 15a in the loading shoe 11a thus define a circumferential pressure space 22a between the mating piece 17a, inside the cavity 24a. The through-piece 17a is centrally formed with a through-pressure oil passage 23a, which thus communicates with the pressure oil passage 9 formed on the roll shaft 3. An axial back-pressure passage 9 'is further formed on the roll shaft 3. 9 ", which communicates with the counterpiece 17a through an axial channel 25a and a transverse channel 26a formed in the annular pressure space 22a.

The operation of the deflection-controlled roller 1 provided with the hydraulic loading elements 10a according to Fig. 3, e.g. according to Figs. 1 and 2, is in principle as follows. First, it is clear that each of the hydraulic load elements of the deflection-adjusted roll 1 according to Fig. 2 is as shown in Fig. 3. As the deflection-controlled roll 1 • ·: '·· rotates, the nip N formed by said roll 1 and the counter roll 6 is loaded by means of hydraulic loading elements 10,10a by passing pressure oil through the pressure oil channels 9 • ·: to each hydraulic hoisting element 10,10a. The pressurized oil thus passes from the pressurized oil channel 9 formed on the shaft 3 to the counterpiece 17a formed from the compressed oil channel 9a to the shaft 3 to the bottom of said hollow portion 24a of the cavity 24a formed in the load shoe 11a. , wherein said compressed oil loads the load shoe 11a against the inner surface 4 of the roll shell.

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In addition to the axial counter-pressure channel 9 'formed in the roll shaft 3, oil at a constant pressure is preferably fed through the connecting channel 9 "and the counterpiece 17a and the transverse channel 26a to the counterpiece 17a and to the counterpiece 17a it • · • 1 · 102003 8 and the annular pressure space between the load shoe 11a, the pressurized oil supplied to this annular pressure space 22a exerting a force opposite to the load force of the load shoe 11a, which tends to pull the load shoe 11a off the roll shell connected to the same and common back pressure channel 9 ', the back pressure being supplied to each load element 10,10a in the same amount, each load shoe 11a being subjected to the same amount of force in the opposite direction of the hydraulic load Due to this counterforce or back pressure, the pressure oil n supplied to the cavity 24a 10 must be increased by an amount corresponding to the pressure of the nip N in order to obtain a nip pressure of the desired magnitude.

With the arrangement described above, it has thus been possible to increase the load pressure of the hydraulic load elements 10,10a by a factor of ten compared to that the back pressure system according to Fig. 3 15 would not be used in the load elements. Thanks to this higher load pressure, the control accuracy of the nip pressure can be substantially improved. In the hydraulics of the deflection-controlled roll 1, for example, an adjustment accuracy of 1 bar can be of the order of ± 0.5 bar. This means that the adjusted zone pressure of 1 bar can actually be 0.5-1.5 bar. Thus, in conventional solutions with low line loads when operating and using those close to the O pressure; '· · Pressure oil pressures, the error in the adjustment accuracy can be at worst up to 50%. With the solution according to the invention, the operating range of the hydraulic load elements 10,10a can be transferred to considerably higher pressures. Thus, when e.g. hydraulic- • · '. The pressure level of the load elements 10,10a has been raised from the 0 level to the level of e.g. 20 bar by the ice arrangement according to the invention, e.g., the control accuracy remains the same as before, • · t ♦ · · * · 1 1 i.e. ± 0.5 bar, but the error in the control accuracy is then only of the order of 2.5%.

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Since the pressure of the pressurized oil in the arrangement according to the invention is significantly higher • · «• · · *. than in conventional deflection-controlled rollers for small line loads, • · M: 30 gives a pressure oil flow in each hydraulic load element of 10,10a or • · t • · * · · · 1 in each zone Zj-Z4, respectively, significantly higher than the current structures. t · a • · • · a · a 9 102003 max, up to ten times or on the order of 100 times compared to current structures. In this case, the cooling effect of the oil is very significant. Since the roll according to the invention is especially intended to operate with small line loads, the mutual variations of the loading pressures in each zone of the roll ZpZ4 are very slightly different from each other. In this case, a situation is reached in which a constant flow of oil passes through each hydraulic loading element 10a, as a result of which, in the best case, the roll 1 according to the invention is made completely uniform in the cross-machine direction. If the control of the line loads requires it, the new control method according to the invention achieves even an absolute 0 level in the load of the hydraulic load elements 10,10a, which was not possible at all before.

Fig. 4 shows an alternative solution of a hydraulic loading element for a deflection-adjustable roll according to the invention, which is generally indicated in Fig. 4 by reference numeral 10b. Also in Fig. 4, the roll shaft is denoted by reference numeral 15 3, the roll jacket by reference numeral 2 and the inner surface of the roll casing by reference numeral 4. Further, the pressurized oil channel formed on the roll shaft 3 is denoted by reference numeral 9 and the back pressure channel In the case of Fig. 4, the hydraulic loading element 10b comprises a cylinder bore 14b formed in the shaft 3 of the roll, which corresponds to the recess or cavity 14a shown in Fig. 3. Mounted in this cylinder bore 14b is a sleeve 17b fixed to the wall of the cylinder bore 14b by a suitable connection 18b; '·· mään. Inside the sleeve 17b, a piston 30b is movably mounted in the load direction of the load element 10b, to which the load shoe 11b is attached. The pockets of the load shoe 11b «· · .1 are indicated in Fig. 4 by reference numeral 12b and the capillary bores by reference numeral • · *. at 13b. Since in the solution according to Fig. 4 the load shoe 11b and the piston 30b • · · • · 1 '· · 1 25 are not the same piece, they are fastened to each other e.g. by means of screws 31b or the like. In the case of the invention, the fastening is rigid. Further, in the embodiment shown in Fig. 4, the capillary bores 13b are formed in the fixing screws 31b of the load shoe 11b • 1. The piston 30b is sleeve-like in that it comprises an inner cavity 24b, so that in this embodiment of the invention very long capillary bores 13b can be used if necessary, since the screws 31b can freely extend inside the cavity 24b.

• · 1 • «1« • «102003 10 An outwardly directed flange member 15b is formed on the piston 30b, which is sealed against the inner wall of the sleeve 17b by means of a seal 21b. Correspondingly, a flange 19b is formed in the sleeve 17b, which is sealed against the outer wall of the piston 30b by means of a seal 20b. The sleeve 17b, the piston 30b and the flange member 15b and the flange 19b thus delimit the annular pressure space 22b therebetween. As already mentioned, the compressed oil channel 9 communicates with the cylinder bore 14b. Correspondingly, the back pressure channel 9 'is connected to the annular pressure space 22b via a connecting channel 9 "and a transverse channel 26b formed in the wall of the sleeve 17b.

The operating principle of the solution according to Figure 4 is very similar to that shown in Figure 3. Thus, first, the pressurized oil for pressurization is led from the pressurized oil passage 9 to the cylinder bore 14b and further to the cavity 30b of the piston 30b to load the load element against the inner surface 4 of the roll shell 4. From the cavity 30b of the piston 30b The pocket structure of the load shoe 11b may be identical to that shown in Fig. 3.

In a manner similar to that shown in Fig. 3, a pressurized oil is led from the back pressure channel 9 'to an annular pressure space 22b, where the pressure of said pressurized oil produces a force opposite to the load direction of the load element 10b. Thus, when a pressurized oil is introduced into said annular pressure space 22b, the pressure of the pressurized oil for pressurizing the load element 10b must be raised accordingly in order to obtain the desired line pressure at the nip N. • «« • ’according to Figure 4. The operating principles of the solution 1 and the advantages achieved by the structure are thus consistent with what was described above in connection with Fig. 3.

Fig. 6 shows a further alternative embodiment of a hydraulic load element for a deflection-adjustable roller according to the invention, which is indicated here in Fig. 6. generally at 10c. In the embodiment of Fig. 6, the shaft of the roll is denoted by reference numeral 3, the roll casing by reference numeral 2 and the inner surface of the roll casing by reference numeral 4. The load element 10c comprises a load shoe 11c and a piston 30c attached thereto. which are connected to each other by a piston 30c and a load shoe 1 le · ·; · ’In a manner similar to that shown in Fig. 4, e.g. by means of screws 31c. As in the embodiment of Fig. 102003 11 4, in the example shown in this figure, pockets 12c are formed on the surface of the load shoe 11c, into which oil is introduced through the capillary bores 13c formed in the screws 31c. The piston 30c is sleeve-like in that it comprises a cavity 24c into which the capillary bores 13c extend from the pockets 12c. A cylinder bore 14c is formed in the roll shaft 35, which communicates with an axially compressed oil passage 9 formed in the roll shaft, through which the pressure oil for the hydraulic loading elements 10c is led to the cylinder bore 14c. A sleeve 17c is fitted in the cylinder bore 14c, which is fixed to the wall of the cylinder bore 14c by means of a suitable connection 18c. A flange member 15c is slidably formed at the lower end of the piston 30c, which is slidably sealed to the inner surface of the sleeve 17c by means of a seal 21c. Correspondingly, a flange 19c is formed at the upper end of the sleeve 17c, which is slidably sealed to the outer surface of the piston 30c by means of a seal 20c. The piston 30c, the sleeve 17c, the flange member 15c and the flange 19c thus delimit an annular space 22c similar to that already shown in connection with the embodiment of Fig. 4.

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However, in the embodiment of Fig. 6 no oil is introduced into this annular space 22c, but in this embodiment a compression spring 32c acting in the axial direction of the piston 30c is arranged in said annular space 22c, e.g. a coil spring according to Fig. 6. Said spring 32c provides a force in the load element 10c opposite to the load direction of the load element 20, which thus tends to pull the load shoe 11c off the inner surface 4 of the roll shell. As a result, there is also a piston 30c in the embodiment of Fig. 6. due to the spring force, a higher pressure • · i i is supplied in its cavity 24c than would be the case without said spring. When applying the hydraulic load element according to Fig. 6 to the deflection-adjustable roll 1 according to the invention, an identical spring 1 I · ** '32c must of course be used in each load element 10c so that a constant counterforce is applied in each load element. . At least the load elements 10,10c in each zone Zj-Z4, which are connected to the same pressure channel 9, must be provided with an identical load spring 32c. Spring 32c I · I «· · '. instead, another mechanical force member may be used to provide a counterforce corresponding to the force of the spring »32.

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The invention has been described above by way of example with reference to the figures of the accompanying drawing. However, the invention is not limited only to the examples shown and described in the figures, but the invention can also be implemented in a different way from the figures. Thus, for example, in the embodiment of Figures 3 and 4, instead of the pressurized oil supplied to the annular pressure chamber 22a, 22b, e.g. compressed air can be supplied if there are no problems with the sealing of the annular pressure chamber 22a, 22b. Furthermore, it can be stated that, for example, instead of a mechanical counter-force element according to Fig. 6, such as a spring 32c, it is conceivable to use an inductive or electromagnetic member with which a counter-force is provided to the load elements 10c. In other respects, it should be noted that different embodiments of the invention may vary within the scope of the inventive idea defined in the appended claims.

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Claims (10)

102003 13 A deflection-adjustable roll for forming a nip (N) with a counter-roll (6), said deflection-adjustable roll (1) comprising a stationary roll shaft (3) about which a roll shell (2) is rotatably arranged, the roll shell (2) and arranged between the roll shaft (3) are hydraulic loading elements (10, 10a, 10b, 10c) acting on the inner surface (4) of the roll shell (2) and supported on the roll shaft (3) by means of a hydraulic pressure medium, comprising cylinder bores formed on the roll shaft (3) ( 14b, 14c) or similar cavity spaces (14a) and load shoes (11a, 11b, 11c) resting on the inner surface (4) of the roll shell (2) 10 via an oil film, the piston parts (30b, 30c) of which are movably arranged radially in said cylinder bores (14b). ) or similar cavities, wherein the pressure medium is arranged in a pressure-adjustable manner to be supplied to said cylinder bores or similar cavities. under the piston parts of the load shoes so that the line load in the nip (N) is adjustable according to the pressure of the pressure medium 15, characterized in that a piston part is formed in the piston part (30b, 30c) of the load shoe of each hydraulic load element (10, 10a, 10b, 10c) extending flange member (15a, 15b, 15c) and a counterpart (17a, 17b, 17c) fitted in the cylinder bores (14b, 14c) or corresponding cavities (14a), respectively, having a flange 19a extending radially in the opposite direction to the flange member of the piston part 19c), wherein the piston part (30b, 30c) and the mating piece «·; '·· (17a, 17b, 17c) is slidably sealed relative to each other through said flange members • V (15a, 15b, 15c) and a flange (19a, 19b, 19c) defining an annular space therebetween • · *. *: (22a, 22b , 22c), which is arranged to be influenced by a continuous load in the opposite direction to the load direction of the hydraulic load elements (10, 10a, 10b, 10c), which • · · S * * • · * 25 together with the desired nip pressure determines the hydraulic load elements • · «9 · · * · * '(10,10a, 10b, 10c) the magnitude of the applied load pressure. • 9 • · Deflection-adjustable roll according to Claim 1, characterized in that a load in the opposite direction to the load direction a ·: 30 traced in the hydraulic load elements (10, 10a, 10b) is provided by the hydraulic load elements • «· t: • <« 4 4 * * «« • IM • iaa «aa 102003 14 (10,10a, 10b) with a pressure connected to the annular spaces (22a, 22b) and generating a force in the opposite direction to the load direction. Deflection-adjustable roll according to Claim 2, characterized in that the pressure generating a force in the direction opposite to the load direction of the hydraulic loading elements (10, 10a, 10b) is applied in equal and constant form to the load elements (10, 10a) of each zone of the deflection-adjustable roll (1). to which the load pressure is applied in the same amount. Deflection-adjustable roll according to Claim 2 or 3, characterized in that the pressure generating a force in the opposite direction to the compression direction of the hydraulic load elements (10, 10a, 10b) is applied to each hydraulic load element (10, 10a, 10b) of the deflection-adjustable roll (1) in the same amount and constant. . Deflection-adjustable roll according to one of Claims 2 to 4, characterized in that the pressure generating a force in the direction opposite to the load direction of the hydraulic loading elements (10, 10a, 10b) is provided by means of a hydraulic pressure medium. Deflection-adjustable roll according to one of Claims 2 to 4, characterized in. 1 ·· from the fact that the pressure generating a force in the opposite direction to the load direction of the hydraulic load elements is provided pneumatically. • · • · · • · • · •: .2i Deflection-adjustable roll according to Claim 1, characterized in that a mechanical force element providing a load in the opposite direction to the load direction is arranged on each hydraulic load element (10, 10c) of the deflection-adjustable roll (1). (32), which tends to pull the hydraulic load element • · * ,, 2 load shoes (11c) off the inner surface (4) of the roll shell (2). • · · • · · · · 1 · • «· •» · 1 • · · t: • · · • · · · · · 9 9 9 · • · 2 · 102003 15 Deflection-adjustable roll according to Claim 7, characterized in that the mechanical force element which produces the opposite load is a spring (32c), in particular a helical spring. Deflection-adjustable roll according to Claim 1, characterized in that an electromagnetic force element is arranged in each hydraulic load element (10) of the deflection-adjustable roll (1) in order to produce a load opposite to the load direction of the hydraulic load elements (10). 10 • 1 »t I 9« · · * ♦ · ♦ · • 1 »·» ♦ · «· • · * ♦ • · ♦ • · 1 * ft •« »1; • · «· tt::« · • · • · · t tM • 1 · «·« «· I« »• · ♦ • · ♦ ·« «· i:« · · 9 · · • · • · t · · • · «· •» · 102003 16